Rolling mill support arrangement



April 21, 1970 K. NEUBER 3,507,138

' I ROLLING MILL SUPPORT. ARRANGEMENT Filed June 20, 1967 s Sheets$heet 1 k 97, P i 2 2 FIG. 3

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IN VE N TOR Idfl A/W make x mm April 21, 1970 K. NEUBER I ROLLING MILL SUPPORT ARRANGEMENT s Shets-Sheet 2 Filed June 20, 196'? FIG. 8

INVENTOR v "A ril 21, 1970 KQNEUBER ROLLING MILL SUPPORT ARRANGEMENT 3 Sheets -Sheet 3 Filed June 20, 1967 FIG. 7

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I, INVENTOR United States Patent 3,507,138 ROLLING MILL SUPPORT ARRANGEMENT Kurt Neuber, 86 Westfalenstrasse, 4 Dusseldorf-Rath, Germany Filed June 20, 1967, Ser. No. 647,557 Int. Cl. B21b 31/24 US. Cl. 72-237 7 Claims ABSTRACT OF THE DISCLOSURE An arrangement for producing planar products in a rolling mill. Defiections ordinarily steming from forces exerted upon the rolling members, during the rolling process are compensated through a force and lever arrangement located at each end of the rollers. The curvature ordinarily prevailing in the rolling member and imparting a non-planar surface to the product being rolled, is compensated for by the lever arrangement so that a fully planar product results. The pressures exerted upon the supporting bearings of the rolling members are also transmitted to the lever arrangement which imparts the compensating effects.

Background of the invention When producing fiat material in the form of sheets or strip through rolling processes, by either hot or cold rolling, elastic deformations of the rolls prevail. These elastic deformations result from the condition that greater rolling pressures exist at the center of the roll than at the edges In the past various attempts have been made to correct this condition so that these deformations may be compensated, since they produce defects in the product when planar results are desired. Such attempts in the past have consisted of applying external auxiliary forces to the compensating forces. Such conventional arrangements bearings and roll members so as to apply the necessary were complex, diflicult to maintain, and not fully effective. Accordingly, it is the object of the present invention to provide a compensating arrangement for rolling mills in which the pressure exerted upon the bearings of the rolls isalso transmitted to auxiliary bearings which act upon the ends of the rolls, and impart to the rolls reactive forces which act in a compensating manner.

Summary of the invention impart compensating effects to the roll members so that a fiat or planar product results from the rolling process.

' The novel features which are considered as characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings.

Brief description of the drawings FIGURES 1 through 3 show the loading diagrams which correspond to the condition when the compensating elfects for producing planar rolled products, areal)- plied in the conventional manner.

FIGURES 4 to 6 show the force loading diagrams of embodiments in accordance with the present invention when the compensating effects for producing planar-rolled products are applied through particular arrangements defined through the present invention.

FIGURES 7 to 10 show the structural design corresponding to the loading diagrams of FIGURES 4 to 6, whereby the compensating effects for producing planar rolled products are applied through the novel arrange ments of the present arrangements.

Description of the preferred embodiments The deflection h of a roll, at its center, is determined by the relation where:

P=rolling force L=length of roll from its center to center of support in b=width of roll in cm.

E=modulus of elasticity in kg./cm.

I=m0ment of inertia of roll in cmfi.

with still flat or planar properties. Thus, with the applica-' tion of intermediate pressures and increased lengths of material increased spreading prevails, but with still planar results.

Below a predetermined critical rolling thickness, the material pressed towards the edges of the rolls, is forced again in the longitudinal direction. As a result, the rolled material is no longer planar. The length along the edges thereof will be longer than the length along its central portion. Due to this condition the well known wavy edge appears.

If a planar roll has a convex cross-section under the critical pressure, in accordance with the previous dBfiIll'.

tion, further reductions must be performed in a specific manner. Thus with every further reduction it is essential that the percentage of reduction is equivalent to the per;

centage increase in length at the center and edges of the roll. It is essential that this percentage relationship be maintained absolutely equal in order to obtain planar results.

Three principal concepts prevail in this process:

(1) Below the critical rolling pressure any convexity of the roll may be diminished with every reduction. However, such convexity can never be absolutely eliminated.

(2) The subsequent passes are thereby performed with decreased rolling pressure, implying decreased roll deflections. i

(3) If a planar sheet or strip is to be produced, itis essential that a planar intermediate product be already available above the critical rolling pressure. At the same time, it is' necessary that every pass, Within the critical region,"be'performed with the spacing between rolls entirely planar.

In order to compensate for the deflection of the roll, it was common, in the past, to grind the roll so as to impart a curvature to it. The curvature of a roll, however, can correspond only to a specific rolling pressure P for a given or pre-deterrnined width b. Accordingly, constructions have been developed whereby the deflection of the rolls and the cross-section of the rolled product may be varied between broad limits. The essential characteristics of such construction are that the rolling pins are extended at each of its bearings, and that auxiliary bearings are arranged about these extensions. These auxiliary bearings are subjected to external forces which counter-act the deflection of the rolls, resulting from the rolling pressure. The change in deflection, measured between the edge and center of the rolling mill, due to the action of the forces exerted upon the auxiliary bearings is given by the relationship where:

M=bending moment due to external auxiliary forces in cm./ kg.

K=external auxiliary forces in kg.

a=lever arm of the external auxiliary forces in cm.

b=rolling width in cm.

E=modulus of elasticity in lcg./cm.

I=moment of inertia of the roll in cm.

The corresponding loading diagram is shown in FIG- URE 2. The resulting deflection curve is of a circular nature. Due to the small convexity of both deflection curves, the auxiliary forces K are substantially ideal with respect to the prevailing rolling pressure P for optimum compensation. The composed or superimposed loading diagram is shown in FIGURE 3. The deflection curve is nearly a horizontal straight line, along the width of the rolling mill.

As may be seen from FIGURE 3, the forces exerted by the bearings upon the rolling mill is P/2+K. It should be noted that the magnitude of the external auxiliary forces K are equal to /6: the rolling pressure.

The external auxiliary forces act upon the adjusting screws of the variable space between rolls, as well as upon the structural frame of the rolls. As a result, it is necessary to provide stronger adjusting mechanisms and more rigid rolling frames for supporting the rolling equipment. In order to avoid these disadvantages, designs have also been developed wherein the influence of the external aux iliary forces upon the adjusting screws is counter-acted by compensating forces. However, as a result of this design and of the precedingly described designs, a further disadvantage arises. This is based on the condition that the external auxiliary forces at the extended ends of the rolling mill must be matched to the prevailing compensating forces as well as to the rolling pressure being used.

The fitting or matching of the external auxiliary forces in relation to the prevailing rolling pressure is accomplished in different ways:

(1) Through the rolling mill operator, after he has manually observed that a correction and the external auxiliary forces are required. The disadvantage of this procedure lies in the fact that the unevenness or nonplanar characteristics of the rolled product must be so apparent that the operator can determine their presence through his optical means.

(2) Through the application of a regulated correction,

' as a result of measuring the rolling pressure with a roll ing pressure measuring device, at the beginning of the rolling process. In this procedure, the matching of the external auxiliary forces to the prevailing rolling pressure is also performed somewhat late. Thus, a portion of the rolled product, at the leading edge of the sheet or strip, remains unregulated.

(3) Through the use of an electronic computer which provides the expected rolling pressure, prior to the first pass. The computer applies from this an adjustment in the external auxiliary forces in the proper relationship to the rolling pressure to be used. This is all performed prior to the first pass. Although this method is theoretically without disadvantages, it requires considerable financial investment in an electronic computer.

Accordingly, it is an object of the present invention to produce planar results to the maximum degree possible when rolling. Such planar results are to be independent of the magnitude of the prevailing rolling pressure, and should avoid the requirement for auxiliary external forces. Thus, it is the object of the invention to eliminate the need for matching the external auxiliary forces to the rolling pressure and thereby avoid the requirement for stronger adjustment mechanisms and structural frames, accompanying the presence of such auxiliary forces.

The present invention achieves the object through the replacement of the auxiliary forces K with reaction forces. Through such reaction forces the bearings of the rolls and the members for transmitting the rolling pressure are arranged as counter-acting bearings in the structural frame of the rolls.

Typical loading diagrams in accordance with the present invention are shown in FIGURES 4 to 6. These embodiments may be extended to any number of desired variations. The corresponding constructional arrangements for the roller bearings and the transmission members, are shown in FIGURES 7 through 10. In these figures the reference numeral 1 denotes the working rolls, when using dual arrangements, and supporting rol s when using quadruple arrangements. The main roller bearing is denoted by 2. The auxiliary bearings on the extended rolling pin are designated as 3 and 4. The reference numerals 5, 6 and 7 represent the intermediate linkage of the rolling pressure transmission members. The pressure adjusting screws are 8, and 9 are guidewalls supported from the main bearings on both sides adjacent to the rolls, for the purpose of guiding the members 5 to 7.

The result of all of the embodiments disclosed herein, is a bending moment which produces the best possible planar characteristics of the rolls. In accordance with the present invention, this bending moment is produced only through the rolling pressure itself and the reaction forces in the bearings. The embodiments in accordance with the present invention involve the retention of the rollers and bearings, and an associated mechanical arrangement of levers and transmission members for the rolling pressure exerted upon the rolls, the rolling structural frame, and the adjusting screws.

When one adds Equations 1 and 2, the following result is realized:

The resulting relationship shows that the lever on A is a function of the variable rolling width b.

In accordance with this result, the invention provides for one or more knife-edged supports between the adjusting screws and the roller bearings linked to a lever for the transmission of the rolling pressure. These knifeedged lever or pivots are constructed in an adjustable manner so as to take into account the rolling width. The wear of the rolls during operation also serves to smooth out the curvature of the rolls and produce planar results.

Due to a varying operational program wherein broad as well as narrow rolled products are produced, at the center of the rolling mill, the wear upon the roll, at

the center, is greater than at the ends thereof. The .portion of the-roll which-is subjected to wear and aifects the cross-section of the roll, and the results arising from the deflection, are dependent only upon the state of the roll. Thus, this portion of the roll which becomes worn will vary only over a very extended period of rolling time and is independent of the prevailing rolling pressure.

The effects of the wear conditions of the roll may be compensated by imparting to theroll a pre-stressed or precurved condition. This pre-stressing or pre-deformation of the roll can be varied from time to time to correspond to the accummulated wear. Such compensation may be realized through hydraulic cylinders situated, for example, between the guidewall along the sides of the roll and the auxiliary bearings, on the extended portions of the roll pins. In the same manner, it is also possible to compensate other long-term effects. For example, it is possible to compensate through this means diameter differences in the roll resulting from temperature variations.

The lever designs shown diagrammatically in FIG- URES 4 to 6 correspond to the structural arrangements illustrated in FIGURES 7 to 10. In all of the embodiments the roll 1 is supported by the main bearings 2 and auxiliary bearings 3 with respect to which the bending moment is generated in the commonly known manner. In accordance with the present invention, this is accomplished through the two-armed lever 5 in FIGURE 7. The central pivot point of this lever rests upon the main bearing 2. The outer portion of this lever is linked to the auxiliary bearings 3, by way of a connecting rod 6. The inner portion of the lever 5, on the other hand, is subject to the action of the adjustment screws 8. The configuration of FIGURE 7 corresponds to the loading diagram of FIGURE 4.

In accordance with the embodiment of FIGURE 8, the main bearing 2 is contained within the same housing as the auxiliary bearing 3, in a rather simplified manner. The housing has a lever extension 5 which is acted upon by the adjusting screw 8 so that the 'desired bending moment is generated.

In accordance with the embodiment of FIGURE 9, a transverse member 9 is provided to which the lever 5 is secured at its central pivot point. The inner end of the lever 5 transmits the pressure exerted by the adjusting screw onto the main bearing 2. The outer end of the lever 5 acts upon a reversing lever 7 which is similarly secured pivotably to the transverse member 9. The reversing lever 7 is linked to the auxiliary bearing 3 by means of the connecting rod 6. This particular embodiment corresponds to the loading diagram of FIGURE 5.

The embodiment of FIGURE 10 shows a construction wherein a supporting bearing 4 is interposed between the main bearing 2 and the auxiliary bearing 3. This supporting bearing 4 serves as a means of support for the lever 7, as in the configuration of FIGURE 9. Thus in accordance with the design of FIGURE 10 it is possible to eliminate the transverse member 9.

In the preceding embodiments, the levers may be made adjustable along their longitudinal directions so that they may be appropriately fitted to a bearing strip width.

It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types of rolling mills differing from the types described above.

While the invention has been illustrated and described as embodied in rolling mills, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the following claims. I

What is claimed as new and desired to be protected by Letters Patent is set forth in the appended claims.

I claim:

1. In a rolling mill, the combination comprising a roll member for rolling material, said roll member having opposite ends; a pair of main bearings respectively located inwardly spaced from said opposite ends of said roll member and supporting the same turnably about its axis; a pair of auxiliary bearings respectively located outwardly of said main bearings and respectively surrounding said roll member in the region of said opposite ends; a pair of adjustable pressure means cooperating with said main bearings for pressing the latter in a first direction increasing the pressure exerted by said roll member on the material to be rolled; and mechanical force transmitting means between said pressure means and said auxiliary bearings for transmitting part of said pressure exerted by said pressure means to said auxiliary hearings in a direction opposite to said first direction so as to impart to said roll member a bending moment which is opposed to the bending moment imparted to said roll member during rolling of material.

2. The combination as defined in claim 1, wherein said last-mentioned mechanical force transmitting means comprise a lever arrangement between each of said adjustable pressure means and the respective auxiliary hearing.

3. The combination as defined in claim 2, wherein said adjustable pressure means comprise adjusting screws.

4. The combination as defined in claim 3, wherein said lever arrangement comprises a two-armed lever pivotally mounted intermediate its ends on the respective main bearing and being engaged at one end thereof by said adjusting screw and a connecting rod connecting the other end of said two-armed lever to the respective auxiliary bearing.

5. The combination as defined in claim 3, and including a transverse member extending along said roll member, and each lever arrangement comprising a two-armed lever pivotally mounted in the region of a respective end of said transverse member, said two-armed lever engaging with one end thereof the respective main bearing and being engaged intermediate its ends by the respective adjusting screw, a reversing lever pivoted intermediate its ends on said transverse member and engaging with one end thereof the other end of said two-armed lever, and a connecting rod connected at opposite ends to the other end of said reversing lever and the respective auxiliary bearing.

6. The combination as defined in claim 3, and including a secondary hearing interposed between each of said main bearings and the auxiliary bearing adjacent thereto, and wherein each of said lever arrangements comprises a two-armed lever pivotally mounted intermediate its ends on said secondary bearing, balancing means interposed between the respective adjusting screw and one end of said two-armed lever and the respective main bearing in such a manner that the pressure exerted by said adjusting screw is substantially evenly distributed to said main bearing and to said one end of said two-armed lever, and an abutment on the respective auxiliary bearing engaged by the other end of said two-armed lever.

7. The arrangement as defined in claim 2, wherein each of said lever arrangements comprises at least one two-armed lever the position of which is adjustable in longitudinal direction of said roll member.

(References on following page) 7 8 v V. References Cited 1 3,364,715 1/1968 OBrien 72245 UN ST P 3,442,1 9 5/1969 DlOlOt 72240 2,897,538 8/1959 Shapiro 61 a1. 72245 CHARLES W, LANHAM, Primary Examiner 3,171,305 3/1965 Stone 72-245 3 250 105 5 1 Stone 7 5 MUSTAIK'IS, Assistant Examine! 

